Vehicle seat

ABSTRACT

The present invention relates to a vehicle seat having a seat part and a backrest, wherein the seat part and the backrest can be adjusted relative to one another by means of an adjustment mechanism, wherein a base plate which holds the adjustment mechanism is provided, wherein the base plate has at least two passage openings through which the base plate is connected to the seat part by means of in each case one fastening means, wherein one of the passage openings is in the form of an elongate hole.

BACKGROUND

The invention relates to a vehicle seat having a seat part and abackrest, as well as a vehicle having such a seat.

A vehicle seat generally comprises a backrest for supporting the back ofa vehicle occupant sitting on the vehicle seat in the normal position.The backrest is able to be adjusted by means of an adjustment mechanismrelative to the seat part of the vehicle seat into a position which iscomfortable for the vehicle occupant. The backrest may also be providedwith a head restraint which is arranged in a rigid or relativelypivotable manner with regard to the backrest.

Generally, the adjustment mechanism is arranged on a base plate which isfastened by means of a screw connection to the seat part. The base plateand the seat part in each case generally have at least two passageopenings which are arranged adjacent to one another in an approximatelyhorizontal plane and into which fastening means engage.

In the event of rear-end collisions in which a vehicle strikes againstthe rear of a vehicle which is stationary or moving slowly, the inertiaof the vehicle occupants relative to the vehicle seat leads toacceleration of the vehicle occupants in the relevant vehicles,potentially resulting in severe injuries of the cervical spine(so-called whiplash injury) when there is no support of the head.

It is known from the prior art to provide head restraints which areintended, for example, to retain the head when it moves backwards. Inthis case, the resilience of the head restraint or the mounting thereofmay result in said head restraint or the mounting thereof pivotingforward and then rearward. This rebound is undesirable.

SUMMARY

It is the object of the present invention to specify a vehicle seathaving improved properties with regard to reducing the speed of impactto the rear of the head during a rear-end collision.

The object is achieved according to the invention by a vehicle seathaving a seat part and a backrest, wherein the seat part and thebackrest can be adjusted relative to one another by means of anadjustment mechanism, such that a base plate receiving the adjustmentmechanism is provided with a slot which, in the event of an impact onthe rear of the vehicle or the rear of a vehicle driving in front, dueto the inertia of a vehicle occupant sitting on the vehicle seat, causesthe backrest to be adjusted to a limited extent counter to the directionof the impact force acting on the vehicle, so that the acceleration ofthe vehicle occupant resulting from the rear impact is at least reduced.

In one possible embodiment, the slot is configured such that, in theevent of an impact on a vehicle, in particular a rear impact, under theaction of the force of the vehicle occupant, in particular the backregion thereof, the backrest is adjusted to the rear to a limited extentcounter to the direction of travel. The path of this adjustment ispredetermined by the length of the slot. By means of an energyabsorption element in the form of a deformable link plate, the impactenergy produced during the impact of the vehicle occupant on thebackrest is in this case at least partially absorbed.

In a further embodiment, a ramp-shaped drive element is provided, saiddrive element engaging in the deformable link plate and contributing tothe at least partial absorption of the impact energy produced during theimpact of the vehicle occupant.

In a further embodiment, two link plates which are able to deform, inparticular able to buckle, may be provided, said link plates at leastpartially absorbing the impact energy produced in the event of an impactof the vehicle occupant on the backrest, so that the speed of impact tothe rear of the head may be reduced.

In a further embodiment, the deformable link plate at a first end isfastened to the seat part by means of the front fastening means togetherwith the passage opening of the base plate configured as a slot, whereina second end of the link plate is aligned in an approximately verticaldirection and is connected to the seat part, so that the impact energyproduced in the event of an impact of the vehicle occupant on thebackrest is at least partially absorbed by expansion of the link plate.

The base plate may also be configured such that tolerances arecompensated to a greater extent in an approximately horizontal planethan in the vertical plane. In this case, the screw connection in eachcase has at least two passage openings in the base plate and in the seatpart, said passage openings being configured such that tolerances arecompensated to a greater extent in the approximately horizontal planethan in the vertical plane.

To this end, at least one first passage opening in the base plate or inthe seat part is configured as a horizontally-extending slot, thevertical extent thereof, i.e. the height thereof, corresponding to thediameter of the fastening means, and being only slightly larger than thediameter thereof. The second passage opening of circular configurationhas a diameter which corresponds to the diameter of the fastening meansand is only slightly larger than the diameter thereof.

The compensation of tolerances, in particular component tolerances, isin this case predetermined by the length of the slot in the base plateor the seat part. The height of the slot and thus the extent thereof inthe vertical direction in this case corresponds substantially to thepredetermined nominal size of the fastening means engaging therein. Bythe implementation of such a slot with a greater compensation oftolerances in the horizontal plane than in the vertical plane,undesirable rotation of the backrest about the pivot axis issubstantially avoided. Moreover, in the event of a rear impact, thebackrest is rotated as little as possible.

In this manner, a particularly rigid design of the connection of thebackrest and the seat part is achieved.

DRAWINGS

Exemplary embodiments of the invention are described in more detailhereinafter with reference to the drawings, in which:

FIG. 1 shows schematically an enlarged detail of a vehicle seat in theregion of an adjustment mechanism and a fastening of the adjustmentmechanism,

FIG. 2 shows schematically the vehicle seat according to FIG. 1 with alink plate arranged in the region of the adjustment mechanism,

FIG. 3 shows schematically a sectional view of the adjustment mechanismwith the link plate according to FIG. 2 along the line III,

FIG. 4 shows schematically a sectional view of the adjustment mechanismaccording to FIG. 2 along the line IV,

FIG. 5 shows schematically a sectional view of a second embodiment ofthe adjustment mechanism with the link plate according to FIG. 2 alongthe line III,

FIG. 6 shows schematically a sectional view of the second embodiment ofthe adjustment mechanism according to FIG. 2 along the line IV,

FIG. 7 shows schematically the vehicle seat according to FIG. 1 with athird embodiment of the adjustment mechanism with two link platesarranged in the region of the adjustment mechanism,

FIG. 8 shows schematically a sectional view of the third embodiment ofthe adjustment mechanism with two link plates according to FIG. 7 alongthe line III,

FIG. 9 shows schematically a vehicle seat with a fourth embodiment of anadjustment mechanism and a fastening for said adjustment mechanism,

FIG. 10 shows schematically an enlarged detail of the vehicle seataccording to FIG. 9 in the region of the fastening with a slot forcompensating for component tolerances,

FIG. 11 shows a perspective view of an enlarged detail of the vehicleseat with a fifth embodiment of the adjustment mechanism,

FIG. 12 shows a perspective view of a base plate of the adjustmentmechanism according to the fifth embodiment.

DETAILED DESCRIPTION

Parts which correspond to one another are provided in all the figureswith the same reference numerals.

FIG. 1 shows schematically in a side view an enlarged detail of avehicle seat 1 comprising a seat part 2 and a backrest 3, which on thefront side has a support surface for the back of a vehicle occupant. Thedetail shows the vehicle seat 1 in the region of an adjustment mechanism4 which permits a pivoting movement of the backrest 3 relative to theseat part 2.

In a manner not shown in more detail, the backrest 3 may also beprovided with a headrest which is arranged in a rigid or relativelypivotable manner with regard to the backrest 3.

The seat part 2 and the backrest 3 are able to be adjusted relative toone another by means of the adjustment mechanism 4 which may be blocked.The adjustment mechanism 4 comprises at least one torsion spring D whichin the region of a pivot axis A of the backrest 3, on the one hand, actsthereon and, on the other hand, acts on the seat part 2, whereby thebackrest 3 is arranged pretensioned in a predeterminable position andmay be blocked in said position, so that a defined support surface iscreated for the back of a vehicle occupant.

During normal operation, the seat part 2 and the backrest 3 are rigidlycoupled together. By releasing the blocking, the backrest 3 may bepositioned counter to, or by the spring force of the torsion spring D bepositioned into, a position which is comfortable for the vehicleoccupant sitting on the vehicle seat 1 and may be blocked in thisposition. For example, a conventional handwheel, not shown in moredetail, may be provided for adjusting the backrest 3. By means of theblocking, the backrest 3 is prevented from being tilted to the front orrear during normal operation.

The adjustment mechanism 4 comprises a base plate 5 to which the torsionspring D is fastened. The base plate 5 is fastened by means of at leastone pair of fastening means 6 and 7, for example screws, to the seatpart 2 (shown in FIG. 2).

In this case, the base plate 5 comprises a slot 8 which permits arotation of the backrest 3 caused by a rear impact. The slot 8 in thiscase forms the through-bore for receiving a fastening means 6, inparticular a front fastening means viewed in the direction of travel.The slot 8 is designed to be linear and extends perpendicular to thedirection of travel from top to bottom.

Alternatively, the slot 8 may be designed to be arcuate, in particularas a circular segment. The front fastening means 6 is inserted into theslot 8 and fastened there such that it strikes against one of the stopends 9.1, 9.2, in particular the rear upper stop end 9.1 of the slot 8viewed in the direction of travel.

In the event of an impact to the rear of the vehicle, as a result of theinertia of a vehicle occupant sitting on the vehicle seat 1, the slot 8permits the backrest 3 to be adjusted to a limited extent in thedirection of the arrow R counter to the direction of the impact forceacting on the vehicle. In this case, the adjustment movement isestablished by the length of the slot 8. With an arcuate slot, thepivoting movement substantially corresponds to the angle of rotation ofthe arcuate slot.

In the event of a rear impact, the front fastening means 6 strikesagainst the front lower stop end 9.2 of the slot 8, so that the movementof the backrest 3 is limited.

By such a limited adjustment movement of the backrest 3 in the directionof the arrow R, counter to the direction of the impact force acting onthe vehicle, a defined adjustment of the backrest 3 is permitted, atleast one portion of the energy caused by the rear impact being able tobe absorbed in the path thereof.

To this end, a link plate 10 is provided as an energy absorptionelement. FIG. 2 shows the adjustment mechanism 4 according to FIG. 1with such a link plate 10. The link plate 10 connects the two fasteningmeans 6 and 7.

In the event of an impact, the link plate 10 serves for the plasticdeformation and thus for energy absorption. By absorbing the energyproduced during the impact, by plastic deformation, the speed of impactto the rear of the head may also be reduced.

To this end, the base plate 5 is provided with a drive element 11. Thebase plate 5 and the drive element 11 may also be configured as a moldedpart.

The drive element 11 is centrally arranged on the lower face of the baseplate 5. The drive element 11 comprises a ramp F which forms an obliqueplane. The ramp F of the drive element 11 is formed at a predeterminedangle relative to the plate plane of the base plate 5. For example, theramp F is arranged at an angle of 45°.

In the case of a rear impact and due to the resulting limited movementof the base plate 5 with the drive element 11 comprising the ramp Falong the slot 8, the ramp F of the drive element 11 presses against thelink plate 10 and entrains said link plate upward or vertically relativeto the plate plane of the base plate 5 such that the link plate 10 isplastically deformed, in particular bent.

A whiplash injury may be counteracted by such an absorption of theenergy produced during the impact, as a result of plastic deformationduring a defined adjustment movement and a reduction of the speed ofimpact to the rear of the head.

FIG. 3 shows schematically a sectional view of the adjustment mechanism4 according to FIG. 2 along the line III.

FIG. 4 shows schematically a sectional view of the adjustment mechanism4 according to FIG. 2 along the line IV.

FIG. 5 shows schematically a sectional view of a second embodiment ofthe adjustment mechanism 4 according to FIG. 2 along the line III.

FIG. 6 shows schematically a sectional view of the second embodiment ofthe adjustment mechanism 4 according to FIG. 2 along the line IV.

The second embodiment coincides in the majority of features with theembodiment shown in FIGS. 1 to 4.

Deviating therefrom, in the second embodiment the drive element 11protrudes from the base plate 5 as a tab-like extension, wherein theextension is angled-back at a predetermined angle from the plate planeof the base plate 5.

In the case of a rear impact and due to the resulting limited movementof the base plate 5 with the drive element 11 along the slot 8, thedrive element 11 presses against the link plate 10 and entrains saidlink plate along the plate plane of the base plate 5 such that the linkplate 10 is plastically deformed, in particular bent.

FIG. 7 shows schematically the vehicle seat according to FIG. 1 with athird embodiment of the adjustment mechanism 4 with two link plates 10arranged in the region of the adjustment mechanism 4.

FIG. 8 shows schematically a sectional view of the third embodiment ofthe adjustment mechanism 4 with the two link plates 10 according to FIG.7 along the line III.

The third embodiment coincides in the majority of features with theembodiments shown in FIGS. 1 to 6.

In the third embodiment, for displacing the backrest 3 a conventionalhandwheel or lever, not shown in more detail, may be provided.

The base plate 5 comprises at least one first slot 8 which permits arotation of the backrest 3 caused by a rear impact. The first slot 8 inthis case forms the through-bore for receiving a fastening means 6, inparticular the front fastening means viewed in the direction of travel.

The first slot 8 is designed to be linear and extends perpendicular tothe direction of travel from bottom to top. Alternatively, the slot 8may be designed to be arcuate, as a circular segment. The frontfastening means 6 is inserted into the first slot 8 and fastened theresuch that it strikes against one of the stop ends 9.1, in particular therear upper stop end 9.1 of the first slot 8 viewed in the direction oftravel.

In the event of an impact to the rear of the vehicle, as a result of theinertia of a vehicle occupant sitting on the vehicle seat 1, the firstslot 8 permits the backrest 3 to be adjusted to a limited extent in thedirection of the arrow R counter to the direction of the impact forceacting on the vehicle. The adjustment movement in this case isestablished by the length of the first slot 8. With an arcuate slot, thepivoting movement substantially corresponds to the angle of rotation ofthe arcuate slot.

In the event of a rear impact, the front fastening means 6 strikesagainst the front lower stop end 9.2 of the first slot 8, so that themovement of the backrest 3 is limited.

By such a limited adjustment movement of the backrest 3 in the directionof the arrow R counter to the direction of the impact force acting onthe vehicle, a defined adjustment of the backrest 3 is permitted, atleast one portion of the energy caused by the rear impact being able tobe absorbed in the path thereof.

To this end, two link plates 10 are provided as an energy-absorptionarrangement. FIG. 8 shows the adjustment mechanism 4 according to FIG.7, with two such link plates 10. The link plates 10 are fastened attheir opposing ends in each case by means of the fastening means 6 and 7to the base plate 5 and connect the two fastening means 6 and 7. Theother ends of the link plates 10 are arranged on top of one anothercentrally between the fastening means 6 and 7, and are fastened to thebase plate 5 by means of a fastening pin 14.

In the event of an impact, the link plates 10 serve for the plasticdeformation, in particular by buckling and thus energy absorption. Byabsorbing the energy generated during the impact, the speed of impact tothe rear of the head may also be reduced by plastic deformation.

To this end, the base plate 5 in the detail is provided with a secondslot 12, in which the fastening pin 14 is retained. As shown in FIG. 8,the second slot 12 is of linear configuration and extends substantiallyparallel to the direction of travel. The second slot 12 is incorporatedcentrally in the base plate 5 as a through-bore. The two link plates 10have on their free ends passage openings which are arranged on top ofone another on the second slot 12, so that the fastening pin 14 is ableto engage in the second slot 12 via the passage openings of the two linkplates 10.

In the case of a rear impact and due to the resulting limited movementof the base plate 5 along the first slot 8, the fastening pin 14 pressesagainst the free ends of the two link plates 10 as shown by the actingforce path P, and entrains said link plates along the plate plane of thebase plate 5 and perpendicular to the direction of travel such that thelink plates 10 are plastically deformed, in particular buckled, as shownwith reference to the buckling direction S.

In this case, the link plates 10 are moved as far as the dead centerline L, and at the same time buckled in the buckling direction S,whereby the backrest 3 is adjusted in a damped manner and strikes thestop end 9.2 of the first slot 8.

In the event of a rear impact, the link plates 10 accordingly serve forthe plastic deformation and thus the energy absorption. In this case,during the deflection of the backrest 3 as a result of a rear impact onthe vehicle, the link plates 10 are entrained in the same direction asthe deflection of the backrest 3 in the direction of the arrow R. Inthis case, the two link plates 10 are buckled and deformed. Inparticular, the two link plates 10 are deformed until said link plateshave reached the predetermined dead center line L, wherein the backrest3 is pivoted further until the fastening means 6 abut against the stopend 9.1 of the first slot 8.

By absorbing the energy produced during the rear impact by plasticdeformation during a defined adjustment movement of the backrest 3, thespeed of impact to the rear of the head is reduced and may counteract awhiplash injury.

FIG. 9 shows schematically a vehicle seat 1 with a fourth embodiment ofan adjustment mechanism 4 and a fastening for said adjustment mechanism4.

The adjustment mechanism 4 comprises a base plate 5 to which the torsionspring D is fastened. The base plate 5 is fastened by means of at leastone pair of fastening means 6 and 7, for example screws, to the seatpart 2.

For receiving the fastening means 6, 7, the base plate 5 comprises twopassage openings O1, O2 of which a first passage opening O1 is designedas a slot 8. The passage openings O1, O2 are arranged adjacent to oneanother in an approximately horizontal plane.

The slot 8 extends in this case in the horizontal plane and thus in aplane with the two passage openings O1 and O2. The vertical extent ofthe slot 8, i.e. the height thereof, corresponds to the diameter of thefastening means 6 and is thus designed to fit precisely, in particularto be only slightly larger than, the diameter of the fastening means 6.

The second passage opening O2 is of circular configuration and has adiameter which corresponds to the diameter of the fastening means 7. Thesecond passage opening O2 is thus designed to fit precisely and to beonly slightly larger than the diameter of the fastening means 7.

In other words, the at least two passage openings O1, O2 in the baseplate 5 are configured with the first passage opening O1 formed as aslot 8, such that tolerances are compensated to a greater extent in theapproximately horizontal plane than in the vertical plane.

As an alternative to the configuration of the first passage opening O1as a slot 8 in the base plate 5, a third passage opening O3 of the seatpart 2 corresponding to the first passage opening O1 may be configuredas a slot (not shown).

In a development, either the first passage opening O1 of the base plate5 or the third passage opening O3 of the seat part 2 correspondingthereto, is provided with a thread for receiving the fastening means 6,a screw. The slot 8 is preferably formed in the passage opening O1 orO3, which is designed to be without a thread.

The length of the slot 8 in this case predetermines the degree ofcompensation of tolerances, in particular the component tolerances. Theheight of the slot 8 and thus the extent thereof in the verticaldirection in this case corresponds substantially to the predeterminednominal size of the fastening means 6 engaging therein.

By implementing such a slot 8, either in the base plate 5 or in the seatpart 2, with a greater compensation of tolerances in the horizontalplane than in the vertical plane, undesirable rotation of the backrest 3around the pivot axis A is substantially avoided.

In the event of an impact on the rear of the vehicle, as a result of theinertia of a vehicle occupant sitting on the vehicle seat 1, the slot 8permits the backrest 3 to be able to be deflected, in particular onlyslightly or not at all, to a limited extent in the vertical directionand thus in the direction of action or deflection, as a result of theaccurately fitting design of the first passage opening O1.

FIG. 10 schematically shows an enlarged detail of the vehicle seat 1according to FIG. 9 in the region of the fastening with a slot 8 in thebase plate 5 for compensating for component tolerances.

FIG. 11 shows a perspective view of an enlarged detail of the vehicleseat 1 with a fifth embodiment of the adjustment mechanism 4 and afastening for said adjustment mechanism 4.

The adjustment mechanism 4 comprises a base plate 5. The base plate 5 isfastened to the seat part 2 by means of at least one pair of fasteningmeans 6 and 7, for example screws.

For receiving the fastening means 6, 7, the base plate 5 comprises twopassage openings O1, O2, of which a first passage opening O1 is designedas a slot 8. The passage openings O1, O2 are arranged adjacent to oneanother in an approximately horizontal plane. FIG. 12 shows aperspective view of the base plate 5.

The slot 8 extends in this case in the vertical plane. The horizontalextent of the slot 8, i.e. its width, corresponds to the diameter of thefastening means 6 and is thus designed to fit precisely, in particularto be only slightly larger than, the diameter of the fastening means 6.

The second passage opening O2 is of circular configuration and has adiameter which corresponds to the diameter of the fastening means 7. Thesecond passage opening O2 is thus designed to fit precisely and to beonly slightly larger than the diameter of the fastening means 7.

In other words, the at least two passage openings O1, O2 in the baseplate 5, with the first passage opening O1 configured as a slot 8, areconfigured such that a deflection of the backrest 3 is possible counterto the direction of travel, i.e. to the rear after an impact to thehead.

As an alternative to designing the first passage opening O1 as a slot 8in the base plate 5, a third passage opening O3 of the seat part 2corresponding to the first passage opening O1 may be designed as a slot(not shown).

In a development, either the first passage opening O1 of the base plate5 or the third passage opening O3 of the seat part 2 correspondingthereto, is provided with a thread for receiving the fastening means 6,a screw. The slot 8 is preferably configured in the passage opening O1or O3, which is designed to be without a thread.

A link plate 10 is also provided, said link plate being fastened, inparticular being screwed, to the seat part 2 at a first end by means ofthe front fastening means 6 together with the passage opening O1 of thebase plate 5.

A second end of the link plate 10 is aligned in approximately thevertical direction and connected, for example welded or screwed onto theseat part 2 or positively suspended therein. In the case of a rearimpact and the resulting deflection of the backrest 3, the link plate 10is subjected to a pulling force counter to the direction of travel in arotational direction denoted by the arrow R and is plastically deformedby expansion in a pulling direction Z, so that it absorbs at least aportion of the impact energy.

The first end of the link plate 10 may have a third slot 13 forreceiving the fastening means 6.

The torsion spring D described in the adjustment mechanism 4 is anon-limiting example of an adjustment means. Other adjustment means, forexample an electric motor, may be equally provided.

LIST OF REFERENCE SYMBOLS

1 Vehicle seat

2 Seat part

3 Backrest

4 Adjustment mechanism

5 Base plate

6 Front fastening means

7 Fastening means

8 Slot, first slot

9.1, 9.2 Stop ends of the slot

10 Link plate

11 Drive element

12 Second slot

13 Third slot

14 Fastening pin

A Pivot axis

D Torsion spring

F Ramp

L Dead center line

O1 to O3 Passage openings

P Force path

R Arrow

S Buckling direction

Z Direction of pulling force

1. A vehicle seat comprising a seat part and a backrest, wherein theseat part and the backrest can be adjusted relative to one another by anadjustment mechanism, wherein a base plate receiving the adjustmentmechanism is provided, wherein the base plate has at least two passageopenings through which the base plate is connected to the seat part byone respective fastening means, wherein one of the passage openings isconfigured as a slot.
 2. The vehicle seat as claimed in claim 1, whereinthe passage openings are arranged adjacent to one another in anapproximately horizontal plane, wherein the slot extends in thehorizontal plane.
 3. The vehicle seat as claimed in claim 1, wherein thepassage openings are arranged adjacent to one another in anapproximately horizontal plane, wherein the slot extends perpendicularto the direction of travel from top to bottom or in an arcuate manner,such that a limited adjustment movement of the backrest is possible inthe event of a rear impact.
 4. The vehicle seat as claimed in claim 3,wherein the slot forms the through-bore of front fastening means viewedin the direction of travel.
 5. The vehicle seat as claimed in claim 3,wherein at least one energy absorption element is provided in the formof link plate which is fastened to at least one of the fastening means,such that the link plate is plastically deformed in the event of a rearimpact as a result of the limited adjustment movement.
 6. The vehicleseat as claimed in claim 5, wherein the link plate connects the twofastening means, wherein a drive element is provided on a lower face ofthe base plate, the drive element entraining the link plate upward orvertically relative to a plate plane of the base plate as a result ofthe limited adjustment movement, such that the link plate is bent. 7.The vehicle seat as claimed in claim 6, wherein the drive elementcomprises a ramp which forms an oblique plane relative to the plateplane of the base plate.
 8. The vehicle seat as claimed in claim 6,wherein the drive element as a tab-like extension is angled back at apredetermined angle from the plate plane of the base plate.
 9. Thevehicle seat as claimed in claim 5, wherein two link plates (10) areprovided, the link plates being fastened to the base plate in each caseat their opposing ends by the fastening means, wherein the other ends ofthe link plates are arranged on top of one another centrally between thefastening means and are fastened to the base plate by a fastening pin ina second slot, wherein the second slot extends substantially parallel toa direction of travel.
 10. The vehicle seat as claimed in claim 5,wherein the link plate at a first end is fastened to the seat part bythe front fastening means together with the passage opening of the baseplate configured as a slot, wherein a second end of the link plate isaligned in an approximately vertical direction and is connected to theseat part.
 11. The vehicle seat as claimed in claim 10, wherein thesecond end of the link plate is welded or screwed to the seat part orpositively suspended therein.
 12. The vehicle seat as claimed in claim10, wherein the first end of the link plate has a third slot forreceiving the fastening means.
 13. The vehicle seat as claimed in claim1, wherein the fastening means comprise screws.